Mining machine



Nov. 23, 1943. R. K. JEFFREY MIN'ING MACHINE 4 Sheets-Sheet 1 OriginalFiled July 6, 1934 .5 w R T mw fihpfi mm W, E m

Nov. 23, 1943; K, EFFRE 2,334,770

MINING MACHINE Original Filed Ju 1y 6, 1934 4 Sheets-Sheet 2 l/vvzs/vTOR: R BERT KJEFF R EY,

Nov. 23, 1943. R. K. JEFFREY MINING MACHINE Original Filed July 6, 19344 Sheets-Sheet s A TT'X f/VVENTOR r ROBERTIKJEFFREY,

Nov. 23, 1943'. R. K. JEVFFREY MINING MACHINE Original Filed July 6,1954 4 Sheets-Sheet 4 f/VVE/VTOR ROBERT KJEFFRE A TT'Y Patented Nov. 23,1943 UNITED "STATES TENT QFFI-CE MINING MACHINE ration of OhioOriginal-application July 6, 1934, Serial No.

733,999, now Patent No. 2,263,701, dated November 25, 1941.

Divided and this application November 18, 1938, Serial No. 241,239. InGreat Britain July 28, 1933 2 Claims.

My invention relates to a mining machine of the universal type, and oneof its objects is the provision of improved and efllcient apparatus forcontrolling the operation of a mining machine by hydraulic means,particularly for feeding the mining machine and swinging the cuttermechanism thereof, both during cutting of a kerf and duringtransportation or cramming.

Another object of the invention is to provide improved slow speedfeeding and high speed tramming mechanism for a mining machine,including a hydraulic system.

Still another objector the invention is to provide a new and improvedhydraulic system of control particularly adapted for mining machines.

Other objects of the invention will appear hereinaiter, the novelfeatures and combinations'being set forth in the appended claims.

In the accompanying drawings,

Figs. 1. and 2 placed end to end combine to make a plan view of themachine shown of my invention;

Fig. 3 is a sectional elevational view of the two speed reductiongearing for the truck drive;

Fig. i is a sectional view taken along the line 4-4 of Fig; 3 looking inthe direction of the arrows;

Fig. 5 is a sectional view taken along the line 5-5 of Fig. 3 looking inthe direction of the arrows;

Fig. 6 is a sectional view taken along the line 56 of Fig. 1 looking inthe direction of the arrows;

7 is a piping diagram of the hydraulic system;

Fig. 8 is a sectional View of the control'valve for the turntablehydraulic motors;

Fig. 9 is a plan view of the reduction gearing control valve;

10 is a sectional plan view of the valve of Fig. 9; and

11 is a sectional view of a hydraulic motor control valve,

This application comprises a'division of my application for a Miningmachine, Serial No. 733,999, filed July 6, 1934, now Patent No.2,263,701, dated Nov. 25, 1941.

Referring to Figs. 1 and 2 of the drawings, it will be seen that themining machine comprises a base frame 29, which is supported on a pairof track engaging rear wheels one of which is seen at 2!, and a pair oftrack engaging front wheels 22, the former being mounted on an axle 23iournalled in bushings in an appropriate housing. The frame 29 ismounted on said housing 'by (ill. 262-28) trunnions providing pivotalmovement of said frame 29 relative to said housing and to said rearwheels 2!, 2| along the central longitudinal axis of said machine. Thefront wheels 22, 22 are supported on an axle 25 carried within anappropriate axle housing which is attached to the base frame 20 by apair of pivoted arms, one on each side of said machine, the pivotalattachment between the arms and the frame 29 being provided byappropriate knuckles.

Adjacent their forward ends the arms are provided with piston rods 28,23 (see Fig. 7), which are connected to pistons 29, 29 which extend intocylinders of hydraulic piston motors so, 39 (see Figs. 2 and '7).

By controlling the hydraulic motors 30, 35, the wheels 22, 22 -may beindividually adjusted in elevation relative to the frame 20, therebyadjusting the slope of said frame 29 relative to a horizontal plane.This is useful to level the frame 20 when the machine is mounted on anuneven track and is useful to tilt the frame 2i! about either atransverse or a longitudinal axis.

Mounted upon the frame 20 for pivotal movement about an upright axispositioned substantially midway between the rear wheels 2 I, 2| and thefront wheels 22, 22, and supported by antifriction rollers is aturntable 32. The turntable 32 has on its lower face a track adapted totake the wear between said rollers and said turntable. On the lower faceof the turntable there is provided a downwardly extending drum which isprovided with an external gear (not shown) with which cooperate racksformed on the ends of apair of spaced piston rods 35, 35 (Figs. 1 and'7), which piston rods are associated with pistons of the two pistonmotors 36, 38. It will thus be evident that by controlling said motors36, 36 the turntable 32 may be adjusted about its upright axis to anydesired position and by locking said motors in any adjusted position theturntable will be held in said position against rotation.

Rigidly mounted upon the upper face of the turntable 32 there isprovided a pair of side castings 37, 31, the rear ends of which areprovided with journalled bearings 38, 3d. Extending between thejournalled bearings 33, 38 and loosely journalled therein, is a rockshaft 39. At each side of the bearings 38, 38 there is a bearing 39, 49,which bearings tit form the ends of a plurality of forwardly extendingarms H, M, of which there are four, two at each side of the turntable.Said arms 6!, ll ar provided with bearings d2, 62 at their forward endswhich are rigidly attached to a transversely extending shaft 43. t mayalso be pointed out that the bearings 4|), 40 are keyed to the shaft 39.The shaft 43 extends into journalled bearings in the housing of anelectric motor 44, whereby said motor 44 may rotate on said shaft 43.

Trunnioned between each of the pairs of arms 4|, 4! at each side of theturntable and approximately midway between the shafts 35 and 43 isa,

hydraulic piston motor 45. Each of the piston motors 45 is provided witha piston rod 46 which is pivoted to the adjacent casting 31. It Will-beevident that by adjusting the piston motors 45, the arms 4|, 4| may bepivoted about the rock shaft 39 and thus the forward portion of theelectric motor 44 may be adjusted in elevation. At its rear end themotor 44 is provided with a bracket 41, to which is trunnioned a pistonmotor 43 having a piston rod 49 pivoted to the rear end of the turntable32. It will be evident that the piston motor 48 may beoperated to pivotthe motor 44 about the axis of shaft 43. It may be mentioned that themotor 44 rests between the inner pair of side arms 4|, thus maintainingthe over-all height of the machine as determined by the top of the motor44, at a minimum.

Rigidly attached to the housing of motor 44 is a gear housing 58, withinwhich are appropriate gears which are part of a train which effects adriving connection between the motor 44 and the cutter chain, as will behereinafter described in more detail. The gear housing 50 has adjacentits forward end a downwardly sloping neck, not

visible in the drawings, upon which is journalled a turn-over head A,formed by a casting 5|, which casting 5| is journalled on said neck forrotation about a longitudinally extending and downwardly sloping axiswhen the machine is in the position illustrated in Figs. 1 and 2. Theforward end of the casting 5| terminates in a drum-shaped portion 52.

To provide for turning over said turn-over head A on th aforementionedaxis, the rear portion of said casting 5| has attached thereto a wormgear within housing 49 which is adapted to be driven by a rotating typeof hydraulic motor 53. It will be evident that by controlling therotating motor55. the turn-over head A may be adjusted to any desiredposition about the axis of said aforementioned neck.

Extending transversely of the drum-shaped portion 52 along the centralaxis thereof, is a transverse shaft upon which is mounted for rotation apair of side plates 55, 55 which cover the open ends of said drum-shapedportion 52. Adjust ment of said side plates 55, 55 about the axis ofsaid transverse shaft is provided by a hydraulic piston motor 56 mountedupon the casting 5| and connected to brackets 51, 5'! carried by saidside plates 55, 55 by appropriate connecting links 56, 58. Adjacenttheir bottoms, the side plates 55. 55 cooperate to provide a circularsupporting track which supports the rear plate 59 of a cutter bar 66,upon which rides endless hit carrying cutter chain 54, whereby saidcutter bar 66 may be pivoted with respect to said turn-over head A aboutan upright axis with respect to the plane of cutter bar 66. It will beevident that this axis may be adjusted to and from a vertical positionby adjustment of the side plates 55 as directed by piston motor 56.

To swing the cutter bar 66 about said upright axis, I provide a pair ofhydraulic piston motors 6|, 6|, which are trunnioned to brackets 62, 62carried by side plates 55, 55. Piston rods 63, 63 of said motors 6|, 6|are pivotally attached to opposite sides of the plate 59 by brackets62'. It will thus be evident that by adjusting the piston motors 6|, 6|,the cutter bar 60 may be swung about an axis permanently at right anglesto itself, which axis is at right angles to the transverse axis andintersects both the latter axis and the axis of the turn-over head.

It is also to be noted that the cutter bar 66 may be swung in ahorizontal plane about the axis of the turntable 52 by controlling thehydraulic piston motors 35. 36. It is thus possible to cut a relativelyhorizontal kerf in a plane which has a slight slope to the horizontal byswinging the cutter bar 66 about the axis of the turntable 32 asaforesaid, such slope being predetermined by adjusting the hydraulicpiston motors 36, 35 in a manner previously described. Cutting of a kerfat a slope to th horizontal about the axis of the turn-over head A will,of course, be provided by adjusting the casting 5| by motor 55.

It will be evident that due to the numerous adjustmentspreviouslydescribed, substantially horizontal kerfs can be out from a positionbelow the mine tracks to a very great height or along any planeintermediate the two extremes. It is also possible to cut kerfs at anydesired slope between the horizontal and vertical position. Furthermore,vertical kerfs may be out along parallel planes of an appreciable Widthin a mine room.

Extending rearwardly from the base fram 28 and forming a portionthereof, I provide a supporting platform 64. Upon said platform 64 ismounted a reversible electric motor 65, adapted to be controlled by acontrol box 66 operable by handle 61. Motor 65 is provided with a shaft68, which extends laterally from each side thereof, and at one sidedrives a pump 69 which may be of any desired structure. The shaft 68carries a pinion 10 adjacent its other end, which pinion meshes with agear 1|. The gear drives a two speed hydraulically controlled planetaryclutch and reduction gear mechanism 12 hereinafter described in fulldetail, which drives a pinion 16 at a relatively fast or relatively slowspeed, depending upon how it is operated. The pinion 6 drives a mastergear 11 which is keyed to a shaft 18 (Fig. 6). Loosely journalled onsaid shaft 1-8 is a sprocket 19 which is connected to a sprocket on oneof the rear wheels 2| by a chain 8|. Also loosely journalled on theshaft 18 is a gear 82 which meshes with a gear 83 formed integral with awinding drum 84 about which is wrapped a flexible cable adapted to beanchored in the mine extraneous to the machine to effect slow feedingthereof.

Clutches 85 and 88 are interconnected by rod and are operable from ahandle 81, and when operated in a position to engage the clutch toeffect a driving connection between the shaft 18 and the wheel 2|, rod80 insures that the drum 84 is not in driving relation with said shaft'18. When the clutch 88 is in operating relation to connect the drum 84to the shaft 18, it insures that the wheel 2| is disconnected from saidshaft 18 thus preventing operation of the drum 84 and sprocket 19 at thesame time.

It will thus be seen that by actuating the clutch 85 to effect a drivingconnection between the shaft '18 and a wheel 2|, the mining machine maybe propelled through the mine by the motor 65 at a relatively slowfeeding speed, or at a relatively fast tramming speed, as hereinafterexplained more in detail. The machine may move in either direction ateither the fast or slow speed -by'reversing the direction of rotation ofthe motor "65 Itmay" be pointed out that the 'rear wheels 2| :are bothkeyed to the drive shaft, andthus both of. said wheels are drivingwheels. Furthermore, a

which drives chain and sprocket drive mecha- I nism I4 controlledby'clutch'92. It.may be noted that the clutch 92 has helical teeth toallow the cable from reel J90 to pay out'freely, or to reel in the cableby power as the mining machine is being. moved under power, or it may bepaid out or'reeled in while the mining machine is standing still, as theclutch-i2 is entirely independent inits operation.

.Also mounted upon the platform 64 is a control box 93 for controllingthe electric motor 44. Appropriate electric cables, not shown, connectthe control box 93 and the motor 44.

In addition to those elements previously described, it may be noted thatthere is carried on the platform 64 a distributing valve 94, thefunction ofwhich will be described more in detail hereinafter, and threeoperating valves having handles 95, -96 and 91 for controlling varioushydraulic motors, as hereinafter described in more detail. It may beadditionally mentioned that mounted upon the turntable 32 are fivevalves, having handles 98, 99, I60, IOI and I02, which will also bedescribed more in detail hereinafter.

Before describing in detail the particular hydraulic system comprisingmy invention, attention is directed to Figs. 3, 4 and 5, and to thestructure of the hydraulically controlled planetary clutch andreductiongear mechanism 12. The gear II is keyed to and drives a shaft:53 one end of which is'journalled in the housing of motor 65 and theother end of which is journalled in a shaft I04 which drives gear Itwhich is keyed thereto. Keyed to the shaft IE3 is a spider not whichcarries a pair of diametrically positioned shafts I26, the outer ends ofwhich are rigidly attached together by a bracket Iill. The shafts I06are provided with appropriate journal bearings I08 upon which arejournalled, integrally formed or connected planetary gears Hi9 and II!)which have an unequal number of teeth. As 11 lustrated in the drawings,gears I89 have sixteen teeth and gears I I B have fifteen teeth, thoughthese numbersare not critical.

Journalled loosely upon the shaft 33 is a sun gear ill which meshes withboth of the gears I09. Sun 'gear IN is keyed to a friction drum H2provided with a peripheral groove I I3 adapted to receive a frictionbrake band I M provided with friction brake band'lining material I I5.By reference particularly to Fig. 3 of the drawings, it will be seenthat the brake'band Il l is pro- Vided with a central attaching lug H6having an oval shaped aperture II'i therein through which a supportingrod H8 extends, which rod is supported by an extending arm H9 formedintegral with a bracket I26 which provides a journal bearing I 2I forpreviously mentioned shaft lad. The freeends of the brake band IM areconnected together-byhydraulic piston motor mechanism I22 (see Fig.1),similarin struc- 169. E39 adapted to receive a brake band I 3|proturetoithehereinafter described mechanism I 34, 'andfed bypipe orconduit I25.

Formed integral with the shaft I04 is a ong :shaped member I26 providedwith an integral internal ring gear I2! which continuously meshes withthe two planetary gears I Iii. J ournalled to rotate freely on theexterior of the cup shaped -member 126 is a drum I28 which is providedwith an integral internal ring gear I29 which continuously meshes withthe planetary gears The drum I28 is provided with a groove vid'ed withfriction brake band lining material 32. The brake band I3! is providedwith an attaching lug I33 similar in structure and function to the lugH6 and is provided with a hydraulic piston motor mechanism I34comprising apair of brackets 123 one attached to each of thefree ends ofthe brake band I3I between which extend a helical spring I24 urging thetwo :halves of the brakeband i3I into a non-braking position. The twobrackets I23 are adapted to be forcibly drawn together by a cylinder andpiston form of hydraulic piston motor of a type commonly employed withthe brakes of an automobile which is supplied with hydraulic fluid byway of a'pipe or conduit I35.

It'may be stated that the number of teeth on the ringgears I21 and I29is the same, but this condition is not absolutely essential.

The hydraulically controlled planetary clutch and reduction gearmechanism '52 is operative to effect a two-speed drive between the shaftHi3 and the shaft I04. It may be stated generally that wheneverhydraulic piston motor mechanism i 22 is operating to apply itsassociated braking mechanism a relatively high speed drive will beeffected between said shafts I03 and IE4 to increase the speed of shaftHi4 over that of shaft I63, and in the instant case the ratio will be 1to 1.285. On the other hand, when the hydraulic piston motor mechanismI34 is applied, the speed ratio between the shafts I03 and We issubstantially reduced in the ratio of 16 to 1.

The high speed drive with the hydraulic piston motor mechanism I22applied operates as follows. Upon the operation of said hydraulic pistonmotor mechanism 622 the friction drum II2 will'be stopped gradually by awell understood clutching and braking action common with planetarygearing, whereupon sun gear III will be stationary. Spider H15 being inrotation, will cause the planetary gears I09, I29 to walk around thestationary 'sunlgear Hi. Gears I 09, being rigid with 'gears Hi3, whichalso walk around with spider IE5 and drive the cup shaped member I26 dueto their meshing with ring gear I 2?. Cup shaped member E26 is, ofcourse, integral with shaft I64 and effects a driving action thereof.

As was above mentioned, the ratio of the drive between shafts m3 and N14is 1 to 1.285. This particular ratio is due to the number of teeth onthe gears I69, IN MI and I21, there being fifteen teeth on' gears H6,sixteen teeth on gears I89, fourteen teeth on gear III and forty-sixteeth on gear I27. noted that gear I29 has forty-six teeth also.

In analyzing this high speed power transfer between shafts I63 and I65it may be observed that as spider IUZi rotates, gear I21 would rotate atthe same speed if gears Iii; and I21 had no relative rotation. Thisalone would provides one to one ratio between shafts I93 and I'M.

In passing, it may also be 'However, since gear I II isstationary, thereis in unison with them.

relative rotation between gears Ilfl'and I21 and for each rotation ofthe spider I95 the additional rotation of shaft I94 over that of shaftI93 is equal to the number of teeth on gear I21 T (46), divided into thenumber of teeth on gears H9 (15), multiplied by the ratio between thenumber of teeth on gear I II (14) to the number of teeth on gears I99(16). In this latter connection it is evident that a clockwise rotationof the spider I95, as indicated by the arrow in Fig. of the drawings,will cause gears I99 to rotate about its own axis W of a revolution foreach revolution of said spider I95.

In effecting the low speed drive the hydraulic piston motor mechanismI34 is energized to apply the brake band I 3| which progressively stopsrotation of drum I28 and integral ring gear I29. Therefore, a spider I95rotates, gears I99 walk around gear I29 and, of course, rotate gears Hi!When the spider I95 has rotated through an angle suflicient to rotategears I 99 one complete revolution, or through sixteen teeth, gear I21which meshes with gears H9 will only have rotated through fifteen teethbecause gears H9 only have fifteen teeth. As a consequence, during thiscomplete rotation of gears I99 and H9 there will be relative movementbetween drum I28 and the cup shaped member I26 equal to one tooth. Thespeed reduction ratio will therefore be sixteen to one since there aresixteen teeth on gears I99.

It is, of course, evident that brake mechanisms I22 and 34 should not beapplied together and the hydraulic control system includes a particulartype of control valve for controlling these hydraulic control mechanismsI22 and I34 which precludes their operation at the same time.

Referring particularly to Fig. 7 of the drawings, there is seen acomplete hydraulic system comprising my invention and referring to Figs.8, 9, and 11 there is illustrated in more detail certain of the valvemechanisms shown diagrammatically in Fig. 7.

Leading from a hydraulic fluid reservoir I35 is a feed pipe I31 forfeeding reversible pump 99, having its output connected to pressure pipeor line S. Four interconnected check valves I38, I39, I49 and I4I sointerconnect pipes I31 and S that regardless of the direction ofrotation of pump 99, pipe S is always the pressure pipe. Interconnectingpressure pipe S and return pipe E is a high pressure relief valve I42and a hand operated by-pass valve I43, the latter of which is normallyclosed but which may be open to relieve the load on pump 59 if it isrotating while doing no useful work.

Referring particularly to Fig. 7 it is to be noted that the supply orpressure line S is common to a plurality of control valves havingoperating handles numbered 95 to I92 inclusive. The structure of each ofthese valves is substantially the same and thus a description of onewill suffice for all. One such device is disclosed in detail in Fig. 11and will now be described. Said valve comprises a casing I44 providedwith three chambers I45, I46 and I41. The supply line S leads to thecentral chamber I45 and two branches of the exhaust or return line Elead to the outside chambers I45 and I41. Between the chainbers I45 andI46 is a small outlet chamber I48 leading to an outlet conduit I49, andbetween the chambers I46 and I41 is a small outlet chamber I59, leadingto a conduit I5I.

Extending into the casing I44 for controlling the flow of the fluidpressure medium or hydraulic fluid to and from the conduits I49, I5I isa pair of valve pistons I52 and I53 carried on a shaft I54. An operatinghandle 95 is provided for operating the shaft I54, said handle beingbiased to a neutral position at which pistons I52 and I53 close thechambers leading toconduits I49 and I5I respectively, said bias beingprovided by a spring I56.

hi the neutral position of the valve, the pistons I52 and I53 completelyclose off the small chambers I48 and I59 respectively and thus seal theconduits I49 and I5I. Any hydraulic piston motor which is connected tothese conduits will thus be locked in adjusted position. If the handle95 is moved to the left as illustrated in Fig. 11, the hydraulicpressure from the supply or pressure line S will be directed throughchambers I46 and I48 to the conduit I49, and the conduit I5I will beconnected to the exhaust or return line E, through chambers I59 and I41.If the handle 95 is operated to the position illustrated in dottedlines, Fig. 11, the pistons I52 and I53 will be moved to the right,under which conditions conduit I5I will be connected to the supply orpressure line S through chambers I45 and I59, while conduit I49 will beconnected to the exhaust or return line E through chambers I48 andReturning to a consideration of the complete system as disclosed in Fig.'7, it will be evident that by controlling the handle I92, the rotatinghydraulic motor 53 may be caused to rotate in either direction,depending upon which direction the handle I92 is moved from its neutralposition. Said motor 53 is connected to its control valve throughconduits M911 and I5Ia. The motor 53, of course, controls the turningover of the head A of the mining machine as was previously described.Handle I9I through its control valve controls the two motors 9|, 6|which are always operated in unison and in re-- verse directions throughthe conduits I49bwand I5Ib. Said motors 6|, 6|, of course, control theswinging of the cutter bar 69, as previously described. The valveprovided with handle I99 controls the hydraulic piston motor 56 throughconduits I490 and I 5I0, said motor 56 being operative to adjust thecutter bar 99 about the axis of the transverse shaft extendingtransversely along the axis of the drum-shaped portion 52 as waspreviously described.

Associated with the hydraulic piston motor 59 I also provide a valve I51which may be open to connect the conduits I490 and I5Ic to allow freemovement of the piston rod of said motor 55, even though the valveassociated with the handle I99 is in a closed position. This is usefulwhen the mining machine is employed to cut a vertical kerf while movingalong a curved track, under which conditions the cutter bar 99 isallowed to swing freely on the axis of the previously mentionedtransverse shaft. It will be obvious, of course, that by closing thevalve I51, the motor 59 is under the direct control of the valveassociated with handle I99.

Motors 45, 45 which control the tilting of the cutter bar and theelectric motor 44 about the axis of shaft 39, are controlled by thevalve with handle 99 through conduits I49d and I5Id. These two motorsoperate in parallel and in the same direction for obvious reasons.

The hydraulic piston motor 48 which controls the tilting of the cutterbar 69 and the electric motor 44 about the axis of shaft 43 iscontrolled from the control valvehaving handle 98 through conduits I49eand IIe.

It will, of course, be obviousthat, due to the fact that there is aconduit connected to each end of the motor cylinders 53, 6|, El, 56,.45, 45 and it, said motors are reversible and also will be locked in anyposition to which they are, adjusted when their respective controlvalves are in neutral positions. This also, applies .to the motors 36,3E) and 36, 36.

Said motors to, 36 which control the tilting of the turntable 32 areprovided with separate control valves havin handles 9'5 and 96respectively and are connected to their respective controlvalves byconduits his) and I 5i) and I49g I58 to IN, inclusive, may be closed toinsure that the motors 39, 66 will be locked in position. It

is, of course, evident that individual control of the motors 36, 30 isdesired so that the turntable 32 may be tilted relative to thehorizontal plane along either a transverse or a longitudinal axis of themachine.

The control valve provided with handle 95 controls the two hydraulicpiston motors 36, 36 which adjust the turntable 32 about its uprightaxis, but this control is made variable by the inter-position in thecontrol system of the. dis

tributor 94 shown in detail in Fig. 8.

The description of the operation of said motors 36, 36 under the controlof valve having handle 95 and distributor 9!! will best be understood byreference to Figs. 7 and 8. Assuming thatthe distributor 9& is in theposition illustrated in Fig. 8 and the control valve is in the positionillustrated in Fig. 11, fluid under pressure will be supplied from theline S to conduit I49 bythe control valve handle 95 being moved to itsfull line position shown in Fig. 11. Hydraulic fluid under pressure insaid conduit I 69 will be divided by ports I62 and I63 of distributor 94to conduits I62 and I63. Conduit I62 leads-to the piston rod end of lefthand motor 36 as viewed in Fig. "7, and conduit I53 leads to the headend of the right hand piston motor 36. It is thus evident that pressurewill be applied to the opposite ends of the two motors 36, which willtend to operate them in opposite directions.

The head end of the left hand motor 36 is con-- nected by conduit E64 toconduit I5I through port I65 of the distributor 94 and the piston rodend of right hand motor 36 is connected to conduit I-5I through conduitI66 and port I61 of distributor 94 It will thus be evident that underthese conditions the two hydraulic piston motors 36 are connected inparallel, and thus the fluid delivered by conduit I49 will be dividedbetween 1 them, whereby they will rotate the turntable :32 at arelatively slow speed, but with great power.

This is desirable where the turntable is rotated I branches of theexhaust and return line E are 3 connected to each end thereof, thusinsuring against unequal pressure on the two ends of said piston I68. 7

Said piston I68 is also provided with: three ports I'll HI and I12 whichare operative when the piston IE8 is rotated by handle I13 to aposition,90 from that positionillustrated in Fig. 8,- to provide. directcommunication between con-1 duits I49 and. 32, between conduits IE5 andIE3, and between: conduits i66-and ltl. Under these circumstances fluidunder pressure supplied to the line I lcwill not be divided between theconduits I62 and I63, but will all be: directed to conduit 52 and to thepiston rod endofleft hand motor The piston head end of left hand motor35 will then be connected through conduitv ltd, port HI and conduit I63:to. the head end of righthand piston motor 36. The piston rod end orright'hand motor 36 will then be connected through conduit I66, port I10and conduit fii to the exhaust or return line B via chamber Ml of Fig.11. Under these circumstances the two piston motors 36, 36 will beconnectedinseries and thus. will travel at. afaster rate thanwhenconnected in parallel; This control isparticularly desirable when it isnecessary to adjust the turntable as the machine is being transported ortrammed through the min and' around curves, under which condition, ofcourse, the cutting mechanism is not performing a kerf cutting operationand a greater speed ofoperation, requiring less power, is desired.

It'will, of course, be evident that by operatingthe handle in reversedirections, the direction of rotation of the turntable 32 may bereversed,

and by operating the distributor 94, the speedof rotation of saidturntable may be determined.

In order to permit the turntable 32 to float, which may be desirablewhen cutting a vertical kerf while-the machine is on a curved track asaforesaid,-I provide a-valve I14 between the conduits I49 and I 5!which, when open, willof course, permit free movement of the motors 36,36;

In addition to the hydraulic control motors previously described as partof my system, there conduit I26 leading from valveI'I'I to mechanism-I22, and conduit I35 leading from valve'll'l to mechanism I38.

Referring particularly to Figs. 9 and 10, it isto be noted that thevalve Ill comprises a cas- Y ing I86 having ports NH and I8Z-therein,connected respectively to the exhaust or return line E and the-supply orpressure lines. A chamber I83- connects the ports NH and I62 throughvalve openings I84 and I85, respectively,

which are controlled by pistons 'I86-and' I811, respectively, whichextend outside the casing I86:-

tively are further pistons I88 and' I89, respectively, which controlports E96 and I 9-I,res'pe'ctively, leading to conduits I25 and I35,respectively. The ports E96 andISI alsocommunicate with a dischargechamber I92 connected to a branch of the exhaust or return line E.- Communication between the. ports IQUa'nd-Itl and:

the chamber I62 is. provided by openingsifimand I94, respectively, whichare. cOntrQIIed by-Said" pistons. I88 and :I 89, respectively.

Rigidly attached to pistons I86 and 48-1 respec A control mechanism isprovided for the contral valve I11 which permits pressure to be appliedto only one of the conduits I25 or I35 at a time. To this end I providea single operating handle I95 which is carried on a shaft I96 and whichcarries an elongated aperture I91.

The pistons I89, I81 carry transversely extending pins I98 and I99,respectively, adapted to slide in elongated slots 209 and ZIJI,respectively, in a bracket 292 upon which shaft I96 is journalled forfree longitudinal and rotary motion. The aperture I91 of handle I95 isadapted to cooperate with the pins I98, I99 selectively upon sliding ofthe shaft I99 along its longitudinal axis whereby one or the other ofsaid pistons I86, I81 may be actuated. It is to be particularly notedthat the bracket 292 carries a central partition 293 which requires thatthe pistons I85, I81 be moved to their extreme lefthand position asviewed in Figs. 9 and 10, before the handle I95 can be shifted laterallyfrom actuating connection with one of said pistons to actuatingconnection with the other. It is also evident that only one of saidpistons can be actuated at one time.

With the handle I95 actuated as illustrated in Fig. 10, the piston motorcontrolling mechanism I22 will be operated. This will be due to the factthat pressure from the supply or pressure line S flows through port I82,chamber I83, port I99and conduit I25 to mechanism I22 to operate thebrake band II4 controlled thereby. Under these conditions it will alsobe noted that the conduit I35 will be connected to the chamber I92whereby the fluid in mechanism I 34 may be freely discharged to theexhaust or return line E.

If the handle I95 is operated to the dotted line position of the valveas illustrated in Fig. 9, it will be evident that fluid pressure in thechamber I83 will be cut off from the conduit I25 by the piston I83, andthat said conduit I25 will be in communication with chamber I92 wherebyfluid in the mechanism I22 may be freely discharged 7 to the exhaust orreturn line E. If then the.

handle I95 is moved laterally so that aperture I91 receives pin I99 andpiston I81 is then moved to the'right as viewed in Figs. 9 and 10,pressure from the pressure line S will be communicated to the conduitI35 and to the mechanism I34 through port I9I as controlled by pistonI99. It is thus obvious that the control valve I11 may operate either ofthe hydraulic piston motor mechanisms I22 and I34 to obtain high speedtramming or low speed feeding of the mining machine, or may leave bothin a non-operating condition, but it is impossible to operate both ofsaid mechanisms at the same time.

From the above description of the mining machine and the hydrauliccontrol system therefor,

The electric motor 44 andthe power transmission mechanism between thesame and the endless chain cutter may be relied on to drive theFurthermore, either vertical or inclined cutter chain 54 during kerfcutting feeding move ments either on the pivotal axis of the cutter baror on the axis of the turntable, or rectilinearly parallel to the minetrack forwardly and rearwardly. All such feeding movements are effectedby the truck propelling motor 65 which operates not only the pump 69 butalso the truck propelling mechanism as shown in Figs. 3, 4 and 5.

It will thus be seen that the feeding movements of the kerf cutter areindependent of the driving of the chain kerf cutter. By reason of thisindependence of the operation, the speed of feed will regulate itselfautomatically in accordance with the hardness of the material being cut,

the feed being faster when relatively soft mate-- rial is being cut, andwill be automatically slowed down when relatively hard material isencoun-v tered. When unusually hard material is encountered in the minevein, the speed of feed may be automatically slowed down with safetybecause the hydraulic pressure responsive valve I42 will then act toreduce the pressure in the supply line S and in the feeding hydraulicmotors. This is particularly true with respect to the hydraulic motors6|, for effecting swinging feeding move- Rectilinear nected to the motor65 which is operated in one direction for the forward sumping feedingmovement, and in the opposite direction for the Withdrawal feedingmovement. However, Whether the motor 55 is operated in one direction orthe reverse, the hydraulic connections including the check valvesassociated with the pump as shown in Fig. '7, will enable the pump to befully effective for maintaining full pressure to mechanisms I22 and I34for controlling the planetary gear power transmission mechanism I2 ofthe truck propelling means connected to the motor 65 as shown in Fig. 1.

Quick, accurate and efiicient control of the feeding movements parallelto the mine track will thus be obtained as well as quick, accurate andemcient swinging feeding movements of the kerf cutter on the pivot ofthe cutter bar along the upright axis of the turntable. Such quickness,accuracy and efficiency of control also applies to the hydraulic motors39, 39 for tilting the mining machine on the longitudinal axis I shownin Fig. l, to the motors 45, 45, 48 for tilting the kerf cutter on thetransverse axes 39 and 43, and to the motor 56 for adjusting the kerfcutter transversely of its plane. 7

During transportation of the machine in the mine from one place toanother, the electric motor 65 of Fig. 1 is relied on to operate therear wheels of the truck. For such purpose the. multiple valve 94 ismoved by means of the handle I13 to connect the cylinders 36, 35 in,

The operation of the pump 69 willthen cause the total volume of flowfrom the pump to i series.

enter the first cylinder 35, thereby eifecting relative rapid swingingmovement of the cutter bar on the turntable axis. As hereinbeforeexplained, when the cutter bar is swung on the turntable axis forfeeding movements, the cylinders 36, 38 are connected in parallel whichwill effect a slower but more powerful swinging movement for feedingpurposes because the volume flow from the pump is divided between thetwo cylinders 36, 36.

Obviously those skilled in the art may make various changes in thedetails and arrangement of parts without departing from the spirit andscope of the invention as defined by the claims hereto appended, and Itherefore wish not to be restricted to the precise construction hereindisclosed.

Having thus described and shown an embodiment of my invention, what Idesire to secure by Letters Patent of the United States is:

1. In a mining machine, the combination with a base frame, of aturntable mounted thereon, a supplemental frame carried by saidturntable and mounted to extend forwardly of said base.

frame, traction means for supporting and propelling said base frame, aplatform extending rearwardlyfrom said base frame, an electric motormounted on said platform, hydraulic motor means to swing said turntableso said supplemental frame can avoid mine posts while traveling aroundcurves in a mine during transportation thereof, a hydraulic systemincluding a pump driven by said electric motor and also includingconnections to said hydraulic motor means, and mechanism for effecting adriving connection between said electric motor and said traction meansto propel said mining machine at a transportation speed while saidturntable is operable as aforesaid, said mechanism being operable bysaid hydraulic system.

2. In a mining machine, the combination with a base frame, of aturntable mounted thereon, a supplemental frame carried by saidturntable and mounted to extend forwardly of said base frame, tractionmeans for supporting and propelling said base frame, a platformextending rearwardly from said base frame, an electric motor mounted onsaid platform, hydraulic motor means to swing said turntable so saidsupplemental frame can avoid mine posts while traveling around curves ina mine during transportation thereof, a hydraulic system including apump driven by said electric motor and also including connections tosaid hydraulic motor means, and mechanism for effecting a drivingconnection between said electric motor and said traction means to propelsaid mining machine, said mechanism being operable by said hydraulicsystem.

, ROBERT K. JEFFREY.

